JPS60500412A - Bicycle servo steering device - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] Title of the Invention: Servo steering device for automobiles The present invention is directed to the first aspect of claim 1. Servo steering device (servo steering device, especially servo steering for automobiles) Regarding equipment.

A servo steering device of this configuration is described in German publication No. 3t2237o. It is publicly known. This servo steering device uses hydraulic reaction force for automobiles. Depending on the speed of I can do it. Therefore, the characteristics of the control valve as shown in FIG. 1 are obtained.

During the bark kink, the control valve operates without hydraulic reaction. i.e. steering hand The operating moment of the dollar is the star, and the mechanical center restoring force MX1 of the control valve. All you have to do is win. and all hydraulic arresters] to move the steering wheels. (curve with a small slope). After the car starts running, mH-like center restoration In addition to the force, there is an auxiliary operating force that depends on the pressure generated by the hydraulic anti-noise device. We have to win one game against Nto. This auxiliary operation is based on the speed of the car. Increases as height increases (slow slope curve). As a result, the parking force This makes it easier to operate the parking lot, which also reduces the risk of damage when driving at high speeds. By transmitting the sensation of the force exerted by the wheels to the steering wheel, Even in this region, good characteristics can be obtained. However, the force when parking is mechanically centered. may be smaller than the restoring force. On the other hand, steering correction in the straight-line driving region If correct, the reaction force exerted on the steering wheels will be reduced, so the running speed (at high speeds) will be reduced. In order to maintain driving safety, this force must be completely transmitted to the steering wheel. No. To achieve this, it is necessary to provide a large m44-like center restoring force that corresponds to this. It has to be true. The reason is that the operating moment is small, so the hydraulic support Sustaining power ceases to exist.

The requirement to lower the center restoring force in the bark kink region is due to the strong Servo support force rather than mechanical center restoring force; contradicts the requirement for adult cows. Therefore The setting of the mechanical center restoring force is 1. It is simply based on the reconciliation of two requirements.

Therefore, the uninvented problem is to be able to control not only the oil field reaction force but also the servo support force. Another object of the present invention is to improve a known power steering device.

This object is solved by the features indicated in claim 1. Advantages of the present invention Further advantageous configurations are indicated in the respective dependent claims.

The detailed structure shown in the drawings is the subject of the invention.

By configuring the control valve with a throttle, a mechanical center restoring device with low center restoring force is possible. Since the position can be placed on the surf steering, the force when parking can be reduced. can be kept at a value. generated before the servo support force acts at relatively high vehicle speeds. Due to the sliding hydraulic reaction force, *ii. An anti-hydraulic rotational moment is generated, which has the property of mechanical center restoration.

The present invention will now be explained in more detail with reference to embodiments shown in the drawings. In the figure , FIG. 1 shows the characteristic curve of a control valve according to the prior art.

FIG. 2 shows the characteristic curve of the control valve according to the invention.

Figures 3-7 are cross-sectional views of several embodiments of control valves with servo steering. It is shown together with a schematic representation of other components.

The servo steering device is a valve installed in the steering device (not shown). It has a control valve 1 with a piston 2, the valve piston 2 being located in a valve housing 3. , it is possible to forcibly move the scales through the terminal handle (Figure 3). . The heating medium: from the servo pump 4 through the inflow contact 5 and into the two rings of the housing. There is a thin hole in the groove 6.7. Valve piston 20 Two pistons; 1. % 3.9 is Through the connection point 10.11 and the pipe 12.13, the actuation of both the servo motors 14 It is connected to the chamber i11'-. The annular groove 15 in the center of the housing is connected to the return connection 1. 6 and a return pipe 17 to communicate with a reservoir 18 .

Annular, pipe S is formed between 16.7 and piston groove 8.9; ¥ control ♀ + illusion Two inlet control openings 19 and 20 are formed by this. Inside the eight At the tip of the annular groove 15 in the center and the collar 2 in the center of the piston 2, there is another control valve edge. There are pairs, which form return control openings 22,23.

Reaction chambers 24, 25 are arranged at both ends of the valve piston 2.

The reaction chamber 24.25 is connected to two connection points 28.2 by reaction piping 26.27. The connection point 28.29 connects the inflow control opening 19.20 and the reaction force control opening 22.23. This is Kouma Kimi. Inside the reaction force piping 26.27, there are two biasing tubes in the direction of the reaction force chamber 24.25. A possible check valve 30.3] is provided.

The reaction force control pipe 32.33 drawn out from the reaction force chamber 24.25 is connected at the connection point 34. They are combined to form one common pipe. Inside the reaction force control pipes 32 and 33, there is a reaction force A fixed throttle 36.37 is arranged between the chamber 24.25 and the connection point 34. Distribution The pipe 35 reaches the reservoir 18 via a control 1ff1 member 38.

The control member 38 is described in German Patent No. 2,127,070 (US Pat. No. 36,904). 00 post) or German Utility Model No. 8029580 For example, it can be designed as a specific electro-hydraulic converter. The important thing is A throttle point with a variable throttle cross-section is controlled by the control member 38 to control the reaction force chamber in the pipe 35. A gap is formed between 24 and 25 and the container 18. The cross-sectional area of the automobile Adjusted depending on speed. Instead of connecting the control member 38 to the container 18, a servo port can be used. It can also be connected to the supply part of the pump 3. This actual gun mode has a reaction force chamber of 24.25 This is preferred for the construction and dimensional centering of the cut-off cover, but this is not in accordance with the present invention. This is important, so I won't explain it here.

Connections 10.11 on both sides of the servo motor 14 and reaction piping of the reaction chamber 24.25 Between the connection points 28 and 29 of 26 and 27, crests 39 and 40 are placed respectively. ing. The throttle 39.40 is a housing in which the valve piston 2 is slidably disposed. It is formed between the hollow hole 43 of the ring and the aperture collar 41.42. piston The grooves 8.9 are formed by these aperture collars 41.42 so that the pistons 7s 8A, 8 It is divided into sections B, 98, and 9B, respectively.

Control edge pair of inflow side 1111 opening 19.20 and return control opening 22.23 '+I The pair ll<'i means that when the control valve 1 is in the neutral position, shielding is insufficient.

Is the inflow control opening] 9.20 and the return control opening 22.23 controlled? ffn valve 1 is open in the neutral position. In this case, all the controls of the inflow control openings 19.20 Insufficient shielding of the edge pair is due to the return fee full opening 22.23 restriction in Ha pair shielding. Greater than the scarcity.

According to the embodiment shown in FIG. 4, the control valve 1 is arranged in a rotatable valve housing. The two valve pistons 45 and 46 (J’A) are formed as counter-rotating piston valves. These valve pistons are connected to two pins 4 at the forked end (not shown) of the steering link shaft. 7.48. In other respects, this embodiment This corresponds to the embodiment shown in FIG. The symmetrically arranged functions of the heavy valve piston 2 are as follows: There are holes distributed in half on one side of the valve piston 45,46.

5 Each valve piston 45,46 therefore has a reaction chamber 24,25 at one end thereof. They each have their own eyebrows. Inflow control opening 19, connection part 10 of servo motor 14 , the connection point 28 of the reaction force chamber 24 and the opening 22 of the return control '4111 are connected to the valve screw I/N 35. This is an example. Between these is an aperture collar 41 with an aperture 39. valve The piston 46 correspondingly connects the inflow control opening 20 and the servo motor 14. connection part 11, two connection points of reaction force chamber 25, return flow control opening 23, and aperture collar between them. -42 and aperture 40. Fixed aperture 36.37 and speed dependent reaction force control device The position control member 38 is formed in a manner corresponding to that shown in FIG.

According to the embodiment of FIG. 5, instead of the aperture collar 41, 42, the valve histone 49 ．． Step portions 51 and 52 are formed in 50. Steps 51.52 are located inside the housing. Together with the boreholes 53.54, they form a throttle slit 55.56. According to this configuration For example, the length of the valve piston 49,50 can be shortened. This is the contact of the reaction chamber 24.25. The connection point 28.29 is axially connected to the valve piston 49.50, at least in part by the servo This is because it is in the same plane as the connection point 10.11 of the motor 14. This means that For example, as shown in FIG. This is possible, for example, when it is rotated by 90 degrees.

According to a further embodiment (FIG. 6), the valve piston 45, 46 is moved from its neutral position. The diaphragm collars 41, 42 come into play only when there is a slight movement. Servo motor 14 A further annular groove 57.58 of the housing is formed in the connection part 10.11.

The control edge formed on one end side of the annular groove 47, 48 is such that when the control valve 1 is in the neutral position, Shape the open reaction force control aperture 59.60 with the diaphragm collar 41.420 control edge. has been completed. The control edges of these control openings are such that the valve piston 45, 46 rotates clockwise or When the wheel is deflected in the counterclockwise direction, the reaction force control opening 59. The control opening 22.23711 is closed, and then the inflow control opening 19 is closed. ．． 20 are tuned relative to each other so that they are closed.

[Effect]

Regulation? When the 1ff valve is in its neutral position (Fig. 3.4), the load from Zarho Bomb 4 is The pressure medium flow is divided into two approximately equal flow streams, and these flows are through the control opening 19.20 and then through the return control opening 22.23 to the reservoir 18. flows into. In this way, the left and right halves of the valve piston 2 or the valve piston 45. Dividing the flow evenly through 46 produces a pressure drop equal to the restriction 39.40 . Both sides of the servo motor 14 and the pressure chambers 24,25 are force balanced.

When the control valve 1 is deflected, for example in a clockwise direction, the valve piston 2 in FIG. 4, the upper valve piston 45 moves to the right and the lower valve piston 45 moves to the right. The screw I/N 46 moves to the left.

Insufficient shielding of control opening pair of inflow control opening 19.20 and return control opening 22.23 Due to the different degrees of The pressure conditions at the Causes a strong reaction. As a result, the inflow control opening 19 and the return control valve opening The partial flow through 22 increases and passes through the inflow control opening 20 and the return control opening 23. The partial flow caused by this decreases correspondingly. Therefore, the pressure drop across the throttle 39 increases. , the pressure drop across the restriction 40 is reduced. Therefore, the pressure inside pistons a8A and 9A is Although it does not change much, the contact inside the pistons a8B and 9B and the reaction force chambers 24 and 25 A distinct pressure difference occurs at the junction 28,29.

If the control tll (38 is closed) 1. Pressure difference at the connection points 28, 29 has no effect on the magnitude of the hydraulic reaction force. This is because the check valve 30 is closed. Therefore, the pressure medium at the connection point 28, which is at a higher pressure, is at a lower pressure. This is because it cannot flow to the connection point 29. Therefore, there is no flow in the orifices 36 and 37. The pressure chambers 24,25 are then pressure balanced.

In this operating region, i.e. when the control member 3B is closed, a mechanical centering action is required. Only for use is valid. The control valve operates without any hydraulic reaction force, so it is easy to steer. Even if all the support force is used to move the wheels that are The recommended operating moment for the handle should be greater than the mechanical center restoring force M7° of the control valve. It is not possible to increase the size of the upper penis. This operating state is shown in Fig. 2 according to the characteristic tune vA61. (In Figure 1.2, the horizontal axis shows the pressure difference Δ of the servo motor. p, and the operating moment M4 of the steering wheel is plotted on the vertical axis. lot).

In the operating state where the vehicle speed is high, the control section fJ'38 is opened.

In this case, the pressure medium passes not only through the check valve 30 but also through the check valve 31 and into the pressure chamber 24. ．． 25, passes through the restrictor 36, 37, and then the 22-opened restriction; through which it can drain into reservoir 18. Connection of reaction force control piping 32 and 33 If the control member 38 is opened to such an extent that a pressure of lisano\18 is created at point 34. , the interaction between the reaction force chambers 24, 25 is eliminated. Flow resistance of check valve 30.31 Neglected, the pressure in the reaction chamber 24.25 will be equal to the pressure present at the connection point 28.29. be equal. If the control valve 1 is deflected, the pressure at the connection point 28 will be equal to the flow force described above. due to the pressure at connection point 29, the leftward, i.e. deflection of the control valve A hydraulic rotational moment is generated in the direction that opposes the Control order of the one control opening mentioned above For the sake of clarity, the inflow control openings Z and L are still open, so the servo motor 141 , the resulting pressure drop is negligible, so the pressure is balanced and therefore the force is generated. There's no one. Therefore, the counter-hydraulic rotational moment mentioned above is due to the mechanical center restoring force. It has characteristics.

When the control valve is deflected further, the return control opening 23 is further closed, so that the valve piston The flow is further biased towards the left half of the valve piston 2 (Fig. 3) or the upper valve piston 45 (Fig. 4). This causes a change in Therefore, at the aperture collar 41, the flow rate is larger. Therefore, the pressure drop becomes large. The pressure difference between connection points 28 and 29 (take-out points) is large. It becomes. This flow dynamic continues until the inflow control opening 19 is activated, at which time A differential pressure is created across the servo motor 14 and the control valve is further operated in a known manner.

In FIG. 2, characteristic curve 62 represents the operating curve at high vehicle speeds.

The sum of the central restoring force MX2 in mW and the central restoring force HX□ due to hydraulic pressure is , which is made clear by the longer horizontal portion of the characteristic curve 62 than the characteristic curve 61. Ru.

When the control member 38 is partially closed, it creates a dynamic pressure at the connection point 34, which dynamic pressure is By reducing the pressure drop between the reaction chambers 24 and 25, hydraulic centering is achieved. The magnitude of the source force and hydraulic reaction force also decreases. This is shown in Figure 3 by characteristic curve 63. It is.

The operation of the embodiment of FIG. 5 corresponds in principle to the embodiment of FIG. 3.4.

The effect of the embodiment shown in FIG. 6 is that the flow resistance decreases when the control valve is in the neutral position. This is different from the embodiment shown in FIGS. 3-5. That is, the reaction force control aperture 59.60 is is opened to allow free flow of pressure medium from the servo motor 4 to the reservoir 18. This is because it is possible. The embodiment shown in FIG. 6 when the control valve is deflected. Made 9 The operation is the same as in the embodiment of FIG. 3.4.

In all the embodiments shown in Figures 3 to 6, the control valves are provided with throttles; When the control valve is deflected from the neutral position, the pressure inside the pressure chamber is limited for the time being. is increased and the control valve is further deflected and then tightened to control the differential pressure across the servo motor. It is important to control the

In the embodiment shown in Fig. 7, the position of the aperture collar is the same as in the embodiment shown in Fig. 6. has been changed compared to. In the embodiment described above, the aperture is 39.40 (3.4th ), aperture 55.56 (Fig. 5) and aperture collar 41.42 (Fig. 6) are between the connection 10.11 of the motor 14 and the return control opening 22.23; The aperture collar 64.65 of the valve piston 66.67 in FIG. between the connection 10.11 and the inflow control opening 19.20. This aperture The location of the aperture or aperture collar may be used in the embodiments of FIGS. 3-5.

The operation of the embodiment of FIG. 7 corresponds to that of the embodiments of FIGS. 3 to 6. In this example Even when the control member 38 is opened, if a slight movement is made, the reaction force chamber 2 4. Only a pressure difference within 25 is generated, and during that time there is almost no pressure difference within the servo motor 14. It never changes.

It should be noted that the control order of the control openings is reversed from that of the embodiments of Figures 3-6. be.

In each of the embodiments described above, the course of the desired characteristic curve depends on the aperture cross section and the control Can be adapted to the current requirements by corresponding selection of the control sequence of the openings. Wear.

sign 1... Control valve, 2... Valve piston, 3... Valve housing, 4... Servo Pump, 6... Annular groove of housing, 7... Annular groove of housing, 8.8A , 8B...Piston l wait, 9.9A, 9B...Piston groove, 1o...14 connection part, 11... connection part of river 4, 12... piping, 13 white piping, 14... Servo motor, 15... Annular groove in the center of the housing, 16... Return contact Connection part, 17...Return piping, 18...Reservoir, 19...Inflow side; wholesale opening, 2o...Inflow control opening, 21...Collar in the center of the piston, 22...Return return control opening, 23... return control opening, 24... reaction force chamber, 25.n reaction force chamber, 2 6...Reaction force piping, 27...Reaction force piping, 28...Connection point of 24.26, 29 ...Connection point of 25.27, 3o...Check valve, 31...Check valve, 32... Reaction force control piping, 33... Reaction force control piping, 34... Connection point, 35... Piping, 36. Self-fixing diaphragm, 37... Fixed diaphragm, 38... Control member, 39... Aperture , 40...Aperture, 41...Aperture color, 42...Aperture color, 43... Bore hole in housing, 44... Valve housing, 45... Valve piston, 46 ...Valve piston, 47...Bin, 48...Bin, 49...Valve piston, 5o...Valve piston, 51...Step part, 52...Step part, 53...Housing Bore hole in the housing, 54... Bore hole in the housing, 55... Throttle slit, 56... ... Throttle slit, 57... Annular groove of housing, 58... Annular groove of housing , 59...Return control aperture, 6°...Return control aperture, 61...Characteristic curve, 6 2...Characteristic curve, 63...Characteristic curve, 64...Aperture color, 65...Aperture collar, 66...valve piston, 67...valve piston.

Claims (1)

[Claims] 1. Servo motor, servo pump, rehearsal, and drawing cutting depending on vehicle speed a control valve with an auxiliary connection for a control member with variable area; The control valve includes at least one axially movable valve piston, an inflow connection, and the inflow connection. one connection each for each side of the servo motor between the connection and the return connection and at least two reaction chambers adjacent the end face of the valve piston. , the reaction force chamber has an inflow control opening formed by a pair of control edges and another pair of control edges. control (1"J Return control formed by a pair of edges'41■ The control located between the opening The reaction chambers are hydraulically isolated from each other by fixed throttles. are connected to the common control member through each one of the apertures, and are connected to the reaction force chamber and the control member. and the working chamber of the servo motor belonging to the reaction force chamber of each of the reaction force chambers. In those equipped with a check valve that can be energized in the direction of 4) The connection point (28) between the connection part (10, 11) and the reaction force chamber (24, 25) on both sides of , 29) and the servo Inflow control opening or return adjacent to the connection (10, 11) of the motor (] 4) The insufficient shielding of the control edge pair of the control J111 opening (19, 20i22.23) was solved by the reaction force chamber ( 24, 25) adjacent to the connection point (28, 29); (22, 23; 19.20) system? The lack of shielding of the 1n edge pair was increased. A power steering device especially for automobiles. 2. It is special that the diaphragm (39, 40) is formed by the diaphragm collar (41, 42). A power steering device, particularly for a motor vehicle, according to claim 1. 3. Connect the throttle (55, 56) to the stepped portion (51, 52) of the valve piston (49, 50). A power supply, particularly for a motor vehicle, according to claim 1, characterized in that it is formed accordingly. Steering device. 4. Each aperture collar (41, 42) has a control edge, which control edge is connected to the valve housing. With each one control edge located in the valve, the control is opened in the neutral position of the valve. Claim 1, characterized in that it forms a released reaction force control opening (59, 60). Power steering H0 especially for automobiles as described in item 2 5. The inflow control opening (19, 60) is 20) and the insufficient shielding of the control edge pair of the return control opening (22, 23). A power steering system, particularly for an automobile, according to claim 4, characterized in that: Place. ■